Forging machine

ABSTRACT

A COMBINED MACHINE IS DISCLOSED FOR FORMING THREADED ARTICLES FROM ROD OR WIRE STOCK. THE MACHINE INCLUDES A PROGRESSIVE HEADER OPERABLE TO UPSET BLANKS AND A RECIPROCATING THREAD ROLLER OPERABLE TO THREAD THE BLANKS. THE HEADER INCLUDES A CRANK AND PITMAN DRIVEN RECIPROCATING SLIDE AND THE THREADER INCLUDES A CRANK AND PITMAN DRIVEN THREAD ROLLING SLIDE. A RECIPROCATING BALANCING MASS IS PROVIDED ON THE MACHINE ON THE SIDE OPPOSITE FROM THE THREAD ROLLING SLIDE. THE DRIVES FOR THE FORMING SLIDE, THREAD ROLLING SLIDE, AND RECIPROCATING MASS ARE ARRANGED SO THAT THE THREAD ROLLING SLIDE AND RECIPROCATING MASS COOPERATE TO PROVIDE SUBSTANTIALLY COMPLETE DYNAMIC BALANCE OF THE ACCELERATION FORCES OF THE FORMING SLIDE. THE CRANK SHAFT IS PROVIDED WITH ROTATING ECCENTRIC MASSES ARRANGED SO THAT THE ROTATING MASSES ARE ALSO DYNAMICALLY BALANCED TO A SUBSTANTIAL EXTENT. BECAUSE SUBSTANTIALLY COMPLETE DYNAMIC BALANCING IS PROVIDED, THE MACHINE MAY OPERATE AT HIGHER SPEEDS WITHOUT DAMAGING VIBRATION.

Jan. 19, 1971` R. E. WISEBAKER i 5 Y351555,586

FORGING MACHINE v Filed Nov. 29, 1968 4 Sheets-5heet l /NVENTO/P Jan.y19, 1971 R. E. wlsEBAKER 3,555,58-64 FORGING MAHIN Filed NQvQzQ, 196s 4sheets-sheet 2 Jan 19,1971 R. E. WISEBMQERv l 3,555,5864

FORGING MACHINE 4 Sheets-Sheet 5 Filed NQv.` 29, 1968 Jan. 19, 1971 R.E. wlsEBAKER v3,555,586

FORGING MACHINE Filed Nov. 29, lees 4 sheets-sheet 4 United StatesPatent Oliice 3,555,586 Patented Jan. 19, 1971 ABSTRACT OF THEDISCLOSURE A combined machine is disclosed for forming threaded articlesfrom rod or wire stock. The machine includes a progressive headeroperable to upset blanks and a reciprocating thread roller operable tothread the blanks. The header includes a crank and pitman drivenreciprocating slide and the threader includes a crank and pitman driventhread rolling slide. A reciprocating balancing mass is provided on themachine on the side opposite from the thread rolling slide. The drivesfor the forming slide, thread rolling slide, and reciprocating mass arearranged so that the thread rolling slide and reciprocating masscooperate to provide substantially complete dynamic balance of theacceleration forces of the forming slide. The crank shaft is providedwith rotating eccentric masses arranged so that the rotating masses arealso dynamically balanced to a substantially extent. Becausesubstantially complete dynamic balancing is provided, the machine mayoperate at higher speeds without damaging vibration.

BACKGROUND OF INVENTION 'This invention relates generally to automaticforging machines for forming threaded articles such as bolts, screws,and the like, and more particularly to a novel and improved machine ofthis type which is capable of operating at high speeds without damagingvibration.

PRIOR ART `Combined machines for forming bolts, screws, and the like arewell known. Such machines often include a progressive header whichoperates to progressively form a blank, and a roll threader whichsubsequently threads the blank to form the finished article. An exampleof such machine is described in the U.S. Letters Patent 2,020,65 8 datedNov. 12, 1935. Other known machines combine a multiple blow header, suchas a double blow header, with a threader. Here again, the header forms ablank which is subsequently threaded to form the desired article. A11example of such a machine is described in the U.S. Letters Patent3,116,499 dated Jan. 7, 1964.

In both types of machines a forming slide is driven for reciprocation bya rotating crank shaft through a crank and pitman mechanism. Therefore,there are two categories of acceleration forces which must be balancedto a sufficient degree to permit operation at the desired speed. The rstcategory includes the forces produced by eccentric masses moving withrotary motion and the second category includes the forces produced bythe reciprocating masses.

In the past it has been customary n many instances to provide rotatingeccentric masses which are sized and positioned to provide some dynamicbalance of the reciprocating mass. Since the motion of such balancingmass is dilferent from the motion of the reciprocating mass, suchbalancing systems cannot provide a truly dynamically balanced machine.Therefore, such machines have been provided with large massive frameswhich are able to absorb the imbalance to a sufficient degree to preventdamaging vibration. These machines function well, but cannot be operatedpractically at higher speeds.

In some machines, which are intended for high-speed operation, separatebalancing masses, which move in a reciprocating manner, have beenprovided to separately balance the reciprocating mass of the slide. Suchmachines provide more complete dynamic balancing and are, therefore,capable of operating at higher speeds without requiring the use ofexcessively large frames or the like. However, they do requireadditional mechanism to supply the support and drive for the separatebalancing masses.

SUMMARY OF THE IINVENTION The present invention is directed to a noveland improved combined machine for forming threaded articles whereinsimplified means are employed to provide dynamic balancing so that themachine can operate at higher speeds. In the illustrated embodimentthere are two reciprocating slides, a header slide and a threader slide.The two slides are located and driven so that each slide provides atleast a part of the dynamic balancing of the other side. The machineprovides suflicient dynamic balancing to permit high-speed operationwithout destructive vibration and accomplishes at least part of thebalancing by the use of mechanisms that also have operation functions inthe machine.

The use of the threader slide to provide at least part of the dynamicbalancing of the forming slide simplifies the machine since, in mostinstances, it eliminates the need of at least one reciprocatingbalancing mass having only a balancing function. Similarly the use of aforming slide to provide dynamic balancing of the threader slideprovides the desired balancing function without requiring a separatebalancing mass to balance the threader slide. A machine incorporatingthis invention includes sufficiently complete dynamic balancing topermit highspeed operation of the machine and provides a structure whichis relatively simple and dependable.

DESCRIPTION OF THE DRAWINGS FIG. 1 is a side elevation of a combinedmachine incorporating this invention illustrating the threader sidethereof;

FIG. 2 is a plan view of the machine illustrated in FIG. 1 with certainparts of the machine eliminated for purposes of simplification;

FIG. 3 is a side elevation of the machine illustrated in FIGS. 1 and 2illustrating the side opposite the side illustrated in FIG. l; and,

FIG. 4 is a schematic fragmentary perspective view of the slide anddrive mechanism of the machine.

Referring to FIGS. 1 through 3,` the illustrated machine is particularlyadapted for the manufacture of bolts, screws, and the like. The machineincludes a frame 10 adapted to support the entire machine. Journaled onthe frame 10 is a main crank shaft 11 which is provided with a fly wheel12 at one end. A motor 13 is connected through drive belts 14 to the flywheel 12 to rotate the crank shaft 111.

The crank shaft 11 -is connected through a pitman 16 to reciprocablydrive a forming slide 17 which is supported on the frame 10 by planarbearings assembly 18 for longitudinal reciprocating movement toward andaway from a die breast 19'. The forming slide 17 and die breast 19 areadapted to support cooperating tools and dies which are arranged toprogressively form a `blank, such as a bolt blank, to its desired shape.A transfer mechanism illustrated generally at Z1 in FIGS. 1 and 3 isprovided to progressively transfer the blanks to each die station sothat a blank is located in each die station during each cycle ofoperation and a completed blank is formed during each cycle. Asillustrated in FIG. 2, the machine is provided with three tool holders22a through 22e each of which is adapted to support a forming tool.Therefore, the illustrated machine is a three die machine. it should beunderstood, however, that the machine incorporating this invention maybe provided with a greater or lesser number of die stations.

The machine also includes a pointer mechanism, shown generally at 23,which is operable to point the blanks after the blanks are formed by thetools carried by the forming slide, and before the blanks are suppliedto a roll threader assembly at 24. Reference may be made to thecopending application Ser. No. 781,092, liled Dec. 4, 1968 for acomplete description of a pointer mechanism which may be utilized withthis'machine. The machine is also provided with a stock feed mechanism26 and a knockout mechanism 27.

Journaled on the frame below the crank shaft 11 is an accessory driveshaft 28 which is connected by gearing 29 to rotate with the samevelocity, but in the opposite direction, as the crank shaft 11. Theaccessory drive shaft is provided with cams which operate linkagesarranged to control the operation of the blank feed mechanism of theroll threader assembly 24 and the operation of the pointer 23. Also thetransfer assembly 21 is powered lby a drive shaft 31 connected to theaccessory drive shaft 28 by bevel gears 32. i

The knockout mechanism is driven by a pitman 33 connected at one end toa crank on the crank shaft 11 and at the other end to a reciprocatingcam shaft 34. The drive for the feed rolls 26 includes a linkage 36partially illustrated in FIG. 3 which is powered by movement of thepitman 33. Reference may be made to the copending application Ser. No.784,806, led Dec. 18, 1968 for a detailed description of the transfermechanism 21 and the knockout mechanism 27.

Reference should now be made to FIG. 4 which schematically illustratesthe main machine drive and the various mechanisms which provide thedynamic balancing of the machine. It should be understood that thevarious elements illustrated in FIG. 4 are not shown to scale and thatthe illustration of FIG. 4 is schematic in nature in o1 der to provide aclear illustration of a functional aspect of this invention.

The crank shaft 11 is journaled on axially spaced bearings 41 and 42which are supported on the frame 10 and in` turn support the crank shaftfor rotation about its axis of rotation 43. The forming slide 17 islocated and shaped so that its mass center moves substantially along aline of action or motion 44 which is located along the longitudinalcenterline of the machine substantially midway between the bearings 41and 42. The structure is also preferably arranged so that the line ofaction 44 intersects and is in the same horizontal plane as the axis ofrotation 43. The crank shaft 11 is provided with a centrally locatedeccentric portion 46 around which one end of the pitman 16 extends andwhich provides the main crank of the machine.

As the crank shaft 11 rotates, the rotation of the eccentric 46' fromthe position illustrated in FIG. 4, which is the backward dead centerposition, causes the forming slide 17 to be accelerated forwardly alongthe line of motion 44 toward the die breast and its forward dead centerposition. This acceleration of the slide toward the forward dead centerposition produces a reaction force on the crank shaft 11 tending to urgethe crank shaft rearwardly with respect to the frame. As the slide 17approaches the forward dead center position, it is decelerated by thecrank shaft. This causes a force on the crank shaft in a forwarddirection.

If dynamic balancing means were not provided, these forces would betransmitted by the crank shaft directly to the frame through thebearings 41 and 42. Since the forming slide is relatively heavy andsince the machine is intended for high-speed'opcration, excessivevibration 4 would occur in the absence of dynamic balancing of theseforces.

The dynamic balancing of the forces created by the acceleration of theforming slide 17 is provided by the thread rolling slide 47 incooperation with a reciprocating mass 48. The thread rolling slide 47 islocated outboard of the bearing 41 on one side of the machine and isguided for reciprocation by opposed bearings, schematically representedat 49, mounted on the machine frame. The bearings 49 position thethreader slide so that its mass center moves along a line of action ormotion 51 which is parallel to the line of motion 44, but is spacedbelow the horizontal plane containing the axis of rotation 43 and theline of motion 44.

A balancing element or mass 48 is pivotally supported at 52 on the frameof the machine, outboard of the bearing `42., for oscillatingreciprocation along an arcurate line of action or movement 53 which islaterally spaced from the line of motion 44. The mass 48 is supported bythe pivot 52 on a projection 54 which extends vertically upward from thepivot so that the principal mass moves along an arcurate path 53 whichhas the relatively large radius when compared to the length of movementalong the arc. Therefore, the movement of the mass 48 approximateslinear reciprocating movement along a path horizontally aligned with theaxis 44 and parallel thereto.

The crank shaft 11 is provided with an eccentric bearing portion 56around which a pitman 57 extends to provide the reciprocating drive forthe balancing mass 48'. Similarly, the threader slide 47 is connected bya pitman 58 journaled on an eccentric bearing 59' located at one end ofthe crank shaft 11. The crank eccentrics 56 and 59 are located withrespect to the main crank eccentric 46 so that they are substantiallytherefrom. Therefore, the slide 47 and the reciprocating mass 48 are insubstantially their forward dead center positions illustrated in FIG. 4when the forming slide is in its rearward dead center position.Consequently, the acceleration of both the slide 47 and thereciprocating mass 48 is substantially 180 out of phase with theacceleration of the slide 17 and movement from the position illustratedin FIG. 4 causes rearward acceleration of the slide 47 and mass 48 atthe same time the forming slide 17 accelerates in a forward direction.

The mass of the slide 47 cooperates with the mass of the reciprocatingmass 48 to provide a substantial amount of dynamic balancing of theacceleration forces of the forming slide 17 and the balancedacceleration forces of the forming slide 17 are transmitted by the crankshaft 11 between the respective eccentric portions and are not,therefore, transmitted to the frame through the bearings 41 and 42. Itis recognized that the oscillating reciprocation of the mass 48 alongthe arcurate path 53 does not provide perfect dynamic balancing of thelinear reciprocation of the forming slide 17 along the central axis 44but since the movement of the mass along the arc closely approximateslinear motion, the dynamic balancing of the mass 48 is suflicientlycomplete to permit relatively highspeed operation. Similarly the slide47 is guided for reciprocation along a line of action 51 which extendsslightly below the plane of the axes 43 and 44. The reason for thisvertical displacement is discussed in detail below. It should beunderstood that such vertical displacement prevents the slide 47 fromoperating exactly 180 out of phase with the forming slide 17, but thephase relationship is close enough to provide sufficient dynamicbalancing to permit high-speed machine operation.

The mass of the slide 47 and its stroke is selected so that theacceleration forces produced thereby are approximately equal to one halfthe acceleration forces produced by the forming slide 17. Similarly, themass of the reciprocating mass 48 and its stroke determined by theeccentricity of the eccentric portion 56 is selected so that itsacceleration forces are equal to about one half of the accelerationforces of the forming slide 17. Also the lateral displacement of theslide 47 from the central axis 44 is selected to be substantially equalto the lateral displacement of the line of action 53 from the centralaxis 44 so that the effective moment arms of the accelerating forces arebalanced. With such an arrangement the thread rolling slide 47 and thereciprocating mass 48 provide substantially complete dynamic balancingof the forming slide 17 and the machine frame is not required to absorbany substantial force due to the reciprocating movement of the elements.

Dynamic balance of the rotating eccentric masses is also provided. Theeccentric 56 which drives the reciprocating mass 48 is located on theopposite side of the crank shaft 11 from the main eccentric 46 and,therefore, provides part of the dynamic balance of the rotatingeccentric mass 46. Similarly the eccentric drive 59 for the slide 47 islocated on the opposite side of the crank shaft 11 from the maineccentric or crank section 46 so it cooperates with the eccentric drive56 to provide substantially complete rotary dynamic balance of the maineccentric 46. Here again the fact that the eccentrics 56 and 59 arelocated substantially equidistant and from opposite side of theeccentric 46 minimizes force moments or couples in the machine.

The ily wheel 12 is provided with an eccentric rotary mass 62 which isadjacent to, but substantially 180 out of phase With, the eccentric 63which drives the pitman 33. The size of the mass 62 and its effectiveeccentricity is selected so that it provides dynamic balancing for themass of the eccentric 63 and in addition provides dynamic balancing forthe adjacent portion of the pitman 33 which moves with substantiallycircular or rotary motion around the axis 43. Therefore, the mass 62provides substantially complete dynamic balancing of the eccentric 63and the adjacent portion of the pitman 33. It is again recognized thatperfect dynamic balancing is not achieved, but the dynamic balancingthat is provided is sufficiently complete to permit high-speed operationof the machine without destructive vibration.

In a machine incorporating this invention the eccen trically rotatingmasses are substantially balanced with respect to the axis of rotation43 of the crank shaft 11 and 4are substantially symmetrical in lateraldirections with respect to the central line of motion 44 of the machine.Similarly the reciprocating masses are in substantially complete dynamicbalance since they are substantially 180 out of phase and aresubstantially symmetrical in a .lateral direction with respect to theline of action 44. Therefore, the machine provides sufficient dynamicbalancing to prevent the destructive vibration from being induced in themachine as a result of acceleration forces applied to the crank shaft.The machine frame is sufciently massive to permit it to safely absorbany nonbalanced forces but is much less massive than would be requiredif substantially complete balancing were not provided.

The line of action 51 of the thread rolling slide is preferably locatedslightly below 4the central axis 44 of the machine so that the pitman 58extends slightly in a downward direction toward the threader slide 47when rearward acceleration of the thread rolling slide 47 is initiated.It is at this point in the cycle that the blank is rst fed in betweenthe stationary thread rolling die and the reciprocating thread rollingdie carried by the thread rolling slide 11. Since a certain a-mount ofclearance is normally desirable in planar bearings of the type used toguide the thread rolling die, it is desirable to arrange the mechanismso that the thread rolling slide is loaded toward the lower bearing byits drive to insure that the clearance is always between the upperthread rolling slide bearing and the thread rolling slide at the momentthe blank enters the dies. This insures that the exact proper positionis maintained between the dies even if a substantial amount of clearanceis provided in the slide bearings. Once the blank is started between thedies it tends to maintain the proper alignment between the dies soproper operation is maintained even if the pitman transmits an upwarddirected force during the latter portion of the rolling cycle.

Although a preferred embodiment of this invention is illustrated, it isto be understood that various modifications and rearrangements may beresorted to without departing from the scope of the invention disclosed.

I claim:

1. A forging machine adapted to form threaded articles comprising aframe, a die breast on said frame, a power-driven article forming slidereciprocable in said frame along a line of motion toward and away fromsaid breast, said article forming slide and breast being adapted tocarry cooperating tools and dies operable to form articles, a threaderon said frame adapted to form threads on articles formed by said articleforming slide, said threader including a stationary threader die supporton said frame and a movable threader die support slide reciprocable onsaid frame along a line of motion substantially parallel to the line ofmotion of said forming slide, and drive means connecting both of saidslides for driving said slides in timed relationship so that said slideseach reciprocate through a cycle in the same period of time andaccelerate and decelerate in opposite directions substantiallysimultaneously whereby each slide provides dynamic balancing of at leasta portion of the acceleration forces of the other slide.

2. A forging machine as set forth in claim 1 wherein said drive meansincludes a crank shaft rotatable about an axis perpendicular to saidline of motion of said forming slide, said crank shaft providing a crankportion associated with each slide, and a pitman connecting each slideand its associated crank portion, said crank portions being locatedsubstantially on opposite sides of said axis.

3. A forging machine as set forth in claim 2 wherein opposed bearingsare provided ou said frame to guide said threader slide forreciprocating movement along its line of motion and such line of motionof said threader slide extends to one side of said axis, said pitmanassociated with said threader slide operating to urge said threaderslide in a direction toward one of its bearings as said threader slidecommences to move in a direction away from said axis.

4. A forging machine as set forth in claim 1 wherein said threader slideis positioned on one side of said forming slide, a reciprocating mass ismounted on said frame on the opposite side of said forming slide formovement along a line of motion substantially parallel to the line ofmotion of said forming slide, and said drive means is connected to drivesaid reciprocating mass through a cycle in which said reciprocating massaccelerates and decelerates in substantially the same directionsubstantially simultaneously with said threader slide, said threaderslide cooperating with said reciprocating mass to provide substantiallydynamic balancing of the acceleration forces of said forming slide.

5. A forging machine as set forth in claim 4 wherein said drive meansincludes a crank shaft rotatable about an axis substantiallyperpendicular to said line of motion of said forming slide, said crankshaft providing a crank portion associated with each slide and saidreciprocating mass, and a pitman connecting each slide and saidreciprocating mass to its associated crank portion, said crank portionsassociated with said threader slide and reciprocating mass being locatedon the side of said axis substantially opposite the crank portionassociated with said forming slide.

6. A forging machine as set forth in claim 5 wherein said reciprocatingmass is pivotally supported on said frame for reciprocating motion, theline of motion of said reciprocating mass being arcuate andsubstantially parallel to the line of motion of said slides.

7. A forging machine as set forth in claim 4 wherein said machineincludes power driven accessories, said crank shaft providing anaccessory drive including a crank portion and an associated pitrnanconnected to drive at least some of said accessories in timedrelationship to the movement of said slides, said crank shaft Ibeingprovided with eccentric means to balance said accessory drive.

8. A forging machine as set forth in claim 7 wherein said crank shaft issupported on said frame by bearings spaced axially along said axis onopposite sides of said forming slides and said crankshaft is providedwith eccentric masses arranged to provide substantially complete dynamicbalancing of the rotating masses.

9. A forging machine adapted to form threaded articles comprising aframe, a die breast on said frame, a rotatable crank shaft, a formingslide reciprocable in said frame along a line of motion toward and awayfrom said die breast, a pitman connected between said crank shaft andforming slide operable to reciprocate said forming slide in response torotation of said crank shaft, a reciprocating mass on said frame on eachside of Said forming slide, means connecting said crank shaft and eachreciprocating mass operable to drive said reciprocating masses in timedrelationship with said forming slide so that each reciprocating massaccelerates and decelerates in a direction pposite the acceleration anddeceleration of said forming slide, said reciprocating massescooperating to provide substantial dynamic balancing of the accelerationforces of said forming slide, one of said reciprocating masses being thethreader slide of a roll threading mechanism.

10. A forging machine as set forth in claim 9 wherein said reciprocatingmasses are sized and spaced from said line of motion of said formingslide so that the force couples applied to said crank shaft by saidreciprocating masses are substantially balanced with respect to saidline of motion.

11. A forging machine as set forth in claim 10 wherein said crank shaftis formed so that the acceleration forces p of rotating eccentric massesare substantially dynamically balanced with respect to the axis ofrotation of said crank shaft.

12. A forging machine as set forth in claim 11 wherein said crank shaftis formed so that the acceleration forces of the rotating eccentricmasses are substantially dynamically balanced with respect to said lineof motion of said forming slide.

References Cited UNITED STATES PATENTS 2,020,658 11/1935 Frost 10-122,141,951 12/1938 Criley 10-15 2,767,601 10/1956 Reed 72-445 2,857,15710/1958 Bonquet 10-15 2,970,327 2/1961 Friedman l0-l5 3,116,499 1/1964Friedman 10-11 3,222,913 12/1965 Leopold 72-429 3,229,496 1/1966 Fosteret al. 72-429 3,496,581 2/1970 Haines 10-11 CHARLES W. LANHAM, PrimaryExaminer E. M. COMBS, Assistant Examiner

